BR112016018940B1 - SOLAR TRACKER SET - Google Patents

Abstract

TORQUE LIMITER AND TORQUE LIMITER DEVICES, SYSTEMS AND METHODS INCORPORATING SOLAR TRACKERS. A solar tracker assembly comprises a support column, a torsion beam connected to the support column, an installation mechanism fixed to the torsion beam, a transmission system connected to the torsion beam, and a torsion limiter. connected with an output of the transmission system. When an external force causes a level of torsion along the transmission system exceeding a preset limit, the torsion limiter facilitates the rotational movement of the solar tracker assembly in the direction of the torsion, thus allowing the external force to turn. about a pivot shaft extending through the torsion beam. Example embodiments also include methods of aligning a plurality of arrays of solar trackers.

Description

REFERENCE TO CORRELATED ORDERS

[0001] This application claims priority with reference to US Patent Application Serial No. 61/941754, filed on February 19, 2014, and US Patent Application Serial No. 62/065741, filed on October 19, 2014, each of which is included as full references.

FIELD

[0002] This descriptive report refers to devices, systems and methods of torsion limiter. This descriptive report also refers to slip clutch and torque limiting assemblies.

FUNDAMENTALS

[0003] As the wind acts along a photovoltaic solar tracking (PV) array or along with other mechanically driven positioning systems exposed to external environmental forces, this causes the appearance of positive and negative pressures near the array, which can act independently, cumulatively, or differentially. These wind forces are generally categorized as drag, lift, drawdown force, and pivot moment about the rotational axis. Wind forces vary depending on wind speed, direction, and array tracking angle rotation. These forces are, in general, even greater next to external structures within a wide range of rows.

[0004] Typically, in the case of single-axis solar tracking systems, the drag and lift induced along the tracked arrangement or along with other mechanical systems are resistant at multiple points within the structure. However, as evidenced by existing systems, the pivot moment becomes resistant, typically, at a single point. The resulting torsional forces applied along relatively long torsion tubes or other beam configurations can be large with a tendency to interact with the torsional flexibility of the crawler structure. Counteracting high pivot moment forces at a single point in the structure requires the presence of torsion members strong enough to withstand both the high torque combined with the beam loads of the system without being overly flexible. Pivoting moment forces can be present as static forces or sometimes as dynamic forces known as torsional divergence. If the crawler structural system is flexible in its design, and the torsion is restricted to a single point, torsional divergence and other dynamic forces can occur presenting a substantially increasing load potential along the structure. Therefore, it becomes structurally advantageous to minimize the flexibility of the tracker structure for the reduction or elimination of wind interactions that can give rise to the presence of these dynamic forces.

[0005] Consequently, there is a need for a mechanism aimed at reducing the peak pivot moment force to which an accompanying system is exposed and/or a need to provide conditions for the system to resist moment forces along several points, effectively minimizing or eliminating the harmonic/dynamic forces to which the structure is exposed. Minimizing torsion in the structure increases the beam load capacity of relevant structural members, since the combination of torsion load and beam loading becomes smaller. By limiting the peak torsional force and then providing a mechanism to resist a lower maximum torsional force at multiple points along the structure, structurally lighter components can be incorporated to reduce material weight and cost. cost of solar tracking systems.

SUMMARY

[0006] Exemplary modalities of the present descriptive report alleviate to a great extent the disadvantages of known mechanical systems, such as those of solar trackers, through the incorporation of a torsion limiter, which may in some circumstances comprise of a clutch limiting torque, at the output of a primary gear box, before a track of secondary gear engages on each row of the tracker. Essentially, this comes down to placing a preset torque release mechanism between the torsionally stressed components and the transmitter in each individually connected or motorized tracker row of a tracker system. Exemplary embodiments of this specification advantageously minimize wind-induced torsional forces near the tracker arrangement so as to materially reduce the structural constraints of the tracker system. The material reduction of the structure can result in a considerable reduction in the cost of the tracking system.

[0007] Exemplary embodiments of a torsion limiter act as a torsional force release valve that minimizes pivot moments and eliminates the presence of any significant dynamic forces that may be induced by wind along mechanical systems, such as structures PV tracking. An important function is to release torsion during strong wind events and provide conditions for each row of trackers to move together in a different position until both the disposition moves to a position where the torsional force no longer presents conditions of overcome the pre-set torsional release force, or the arrangement is moved by torsional force to extreme angles of rotation and then restrained along multiple points on the structure. The incorporation of multiple stops along the array at the extreme positions of rotation minimizes the presence of torsional force in any section of the component or structural components resisting torsion.

[0008] In exemplary embodiments, the torque limiter can also act as an overload release regarding the transmission motor input force, if the arrangement cannot move due to an obstruction, such as a heavy load of snow without balance , snow shifts, or sand dunes, or if one or more chained gearsets are faced with an extreme limit stop condition. In this condition, the torque limiting clutch will decouple the input transmission forces from the output forces if the clogging resistance is greater than the torque restriction limit. In exemplary embodiments, the forces that will be released by the torsion limiter comprise both the externally induced pivot moment forces within the arrangement, as well as those from the input drive mechanism, when the input drive forces required for movement of the arrangement are above the torque limiter limit.

[0009] The exemplary embodiments of a solar tracker assembly comprise a support column, a torsion beam connected to the support column, an assembly mechanism attached to the torsion beam, a transmission system connected to the torsion beam, and a torque limiter connected to the transmission system. The solar tracker assembly may include a plurality of support columns and further comprise a stop adjacent to each support column. The torsion beam can be configured to have a balanced center of gravity so that it rotates around the balanced center of gravity. When an external force such as wind induces a level of torsion in the system exceeding a preset limit, the torsion limiter then facilitates rotational movement of the solar tracker assembly in the direction of the torsion, thereby enabling the external force to rotate the assembly about a pivot shaft extending through the torsion beam.

[0010] In exemplary embodiments, the torsion limiter decouples the excess torsion so that the external force is released by enabling the arrangement to move to a second rotational position. Moving in the twisting direction may comprise moving the solar tracker assembly from a first rotational position to at least a second rotational position. In exemplary embodiments, when the external force is large enough, the solar tracker moves to an extreme stop position of the rotational position. The mechanical stop of the maximum rotational position occurs at a maximum rotation angle, then resists at multiple points in the tracking structure, so that the primary torsional strength structural member is ultimately rotationally supported at multiple points. , effectively limiting torsion in the torsion beam structure.

[0011] Movement in the direction of torsion may comprise movement of the solar tracker assembly from a first rotational position to a second or multiple rotational positions. In exemplary embodiments, the solar tracker assembly is restricted in its maximum rotational movement in front of multiple locations distributed along a torsional resistant structure of the solar tracker assembly. The torsion limiter limits the pivot moment around the pivot axis extending through the torsion beam when the tracker is not in the extreme positions enabling the tracker to rotate to release the torsional force and then the multiple stops along the extreme positions that ultimately limit torsion in any one torsion resistant structural member section when the system cannot come to perform any further rotation.

[0012] In exemplary embodiments, the transmission system of the solar tracker assembly comprises a gear assembly including at least one gear wheel. In exemplary embodiments, the gear assembly includes a one-way gearbox and the torque limiter consists of a torque-restricting gear. The torque limiter may further consist of a slip clutch in some embodiments. In exemplary embodiments, the gear assembly includes a friction coupling engaging the gear wheel and the torque limiter is located adjacent the friction coupling. The torque limiter may be located adjacent to the output of a first gear stage of the gear assembly. In other exemplary embodiments, the solar tracker assembly consists of a balanced connected tracker and the torque limiter consists of a linear slide device or a linear clutch linkage. The solar tracker assembly may include a hydraulic system and the torque limiter may be in the form of a pressure release valve along with the hydraulic system. The sun tracker assembly may further comprise a damper incorporated at or near the gear track to control the release of torsional force and retard the momentum of the sun tracker assembly.

[0013] Exemplary embodiments include methods of aligning a solar array comprising a plurality of rows of solar trackers, providing with a torsion limiter individually connected next to each row of solar trackers, where one or more solar trackers meet a rotational limit mechanical that causes the appearance of the torsion level induced by the transmission line next to at least one row of solar trackers exceeding the torsion restriction limit, and the torsion limiter gives conditions for a mechanical limitation where at least one row does not rotate while simultaneously activating the rotation of the other multiple rows of solar trackers. The plurality of solar tracker arrays include multiple connected solar tracker arrays. The mechanical boundary condition of at least one row of sun trackers includes multiple rows of connected sun trackers. The mechanical limit condition of at least one row of sun trackers from the multiple rows of sun trackers creates a level of torsion in the tracker that exceeds a preset limit.

[0014] At least one mechanically limited row does not rotate while the other multiple sun tracker rows rotate and reach their maximum mechanical limit position until the entire plurality of sun tracker rows are no longer rotating. As each row reaches its maximum mechanical limit position, each tracker row stops rotational motion while the other multiple rows of solar trackers rotate and reach their maximum limit positions. When all the ranks of trackers have reached their mechanical limits, then they will all line up.

[0015] The same mechanism that limits and releases the transmission torque before a safety limit is also advantageous if one or more tracker rows are obstructed by external environmental conditions, such as snow displacement, sand dunes or other impediments . The twist limiter can protect the tracked arrangement from damage caused by obstructions, while still allowing the tracker to rotate in a limited motion until the obstruction is cleared.

[0016] In exemplary embodiments, during excessive torsion from external forces, movement in the direction of torsion comprises moving at least one row of solar trackers from a first rotational position to a second rotational position. Moving in the twisting direction may comprise moving at least one row of sun trackers from a first rotational position to multiple rotational positions. In exemplary embodiments, at least one array of solar trackers achieves multiple mechanical constraints at multiple rotational positions or maximum limit positions. Exemplary modalities also comprise the incorporation of a damper close to or next to the torsion limiter to control the release of torsional force and delay the movement of the set of solar trackers.

[0017] In the exemplary modalities of a simple motorized solar tracker set, there is the presence of a support column, one or more torsion beams connected to the support column, a solar module installation system fixed next to one or more torsion beams, a transmission system connected to one or more torsion beams, and an engine brake. The transmission system comprises a bidirectional gearbox having an input and an output, and the engine brake is located adjacent to the input of the bidirectional gearbox. When an external force causes a level of torsion along the transmission system to exceed a preset limit, the engine brake slips, or in case the engine brake is internal to the engine itself, it is activated backwards through of the system, which facilitates the spare drive of the system with the release of torsional force.

[0018] In exemplary embodiments, a gear transmission system comprises a gear assembly including a torque limiting clutch and at least one helical gear wheel. The gear assembly may or may not be contained within the gearbox. When a level of torque in the gear exceeds a preset level, the clutch slips. The gear assembly may include two conical sections engaging the helical gear wheel. In exemplary embodiments, the torque limitation clutch is located next to the two conical sections. The clutch can be adjusted via a thread by varying the spring tension along the conical section. This sliding clutch can assume alternate shapes in the exemplary embodiments and other shapes as needed for different types of gear driven mechanical systems.

[0019] In exemplary embodiments, a solar tracker assembly comprises at least one support column, a torsion beam connected to the support column, containing a pivot shaft extending through the torsion beam, an installation mechanism attached to the torsion beam, one or more solar modules installed adjacent to the installation mechanism, and a clutch box assembly containing a torque limiting clutch and at least one helical clutch wheel. When a torque level at the clutch box exceeds a preset limit, the clutch slips.

[0020] In exemplary embodiments of a gear-driven mechanical system, at least one gear-associated mechanical unit is present, including at least one gear track and a gear drive system engaging with the gear track. The gear drive system comprises a gear set including at least one gear wheel, and a torque limiting clutch located adjacent an output of the gear set and preceding a location where the gear drive system engages with the gear track. When a level of torque to the gear system exceeds a preset level, the clutch slips, releasing torque to the gear driven mechanical unit.

[0021] In exemplary embodiments, the gear assembly includes at least one conical section engaging the gear wheel with the torque limiting clutch located in the conical section. The clutch can be adjusted via a screw that varies the spring tension along the conical section. In exemplary embodiments, there is a mechanical unit driven by a rotational gear. In exemplary embodiments, the gear-driven mechanical unit rotates to a hard stop position near its maximum angle of rotation.

[0022] Exemplary embodiments of a gear-driven mechanical system comprise at least one gear-driven mechanical unit rotating around an axis of rotation and a gear transmission system. The gear driven mechanical unit includes at least one gear track and the gear drive system engages with the gear track. The gear drive system consists of a gear assembly including at least one gear wheel and a torque limiting clutch located adjacent an output of the gear assembly. When a level of torque in the gear assembly exceeds a preset level, the clutch slips, releasing torque to the clutch driven mechanical unit and limiting a pivotal moment about the rotational axis.

[0023] In exemplary embodiments, the torque limitation clutch is located next to the output of a first gear stage of the gear-driven mechanical unit. In exemplary embodiments, the torque limiting clutch is incorporated at the inlet next to the gear track of the gear-driven mechanical unit. The at least one gear driven mechanical unit may comprise of a plurality of gear driven mechanical units. In exemplary embodiments, each gear-driven mechanical unit rotates until it reaches a mechanically limited stop position at its maximum angle of rotation.

[0024] In exemplary embodiments of a solar tracker system, at least one set of solar trackers is maintained rotationally through a torque limitation clutch. The solar tracker assembly includes at least one support column, a torsion beam connected to the support column, a module installation mechanism attached to the torsion beam, and at least one gear transmission assembly connected to the torsion beam. A pivot shaft extends through the torsion beam. The torque limiting clutch engages with the gear drive assembly. When the level of externally applied torque at the gear drive assembly exceeds a preset level, the clutch slips allowing the tracking system to rotate, thereby releasing torque at the sun tracker assembly and reducing the pivot moment. around the pivot axis.

[0025] In exemplary embodiments, the torque limitation clutch is located next to the output of a first gear stage of the solar tracker set. In exemplary embodiments, the torque limiting clutch is incorporated into the gear transmission assembly of the solar tracker assembly. The gear drive assembly may include a main drive gear, the torque limiting clutch being incorporated at the output of the main drive gear. In exemplary embodiments, the solar tracker assembly rotates to engage a mechanical stop at its maximum angle of rotation.

[0026] The solar tracking system may consist of a chained system where the torque limiting clutch is incorporated between an arm connection and the torque tube. The solar tracking system may consist of a balanced connection tracker. In other exemplary embodiments, the solar tracking system is hydraulically driven, and the torque limiting clutch consists of a pressure release valve.

[0027] Consequently, it is observed that torque limiters, torque limiting clutches, gear transmission systems, solar trackers, and related torque release methods can be provided. The devices, systems, and methods described provide for a preset torque release mechanism, thereby reducing or eliminating pivot moments and other dynamic forces within the PV tracking structure. These and other features and advantages will be appreciated from reviewing the detailed description below, along with accompanying figures where reference numerals refer to similar parts throughout.

BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The features and advantages mentioned above in this descriptive report will become evident with reference to the following description taken together with the accompanying drawings where reference numerals represent identical elements and where: Fig. 1A comprises a schematic referring to an exemplary embodiment of a mechanical unit according to the present specification; the Fig. 1B is a schematic of an exemplary embodiment of a mechanical unit in accordance with the present specification; the Fig. 1C is a schematic of an exemplary embodiment of a mechanical unit in accordance with the present specification; the Fig. 1D is a schematic of an example embodiment of a mechanical unit according to the present specification; the Fig. 2 is a process flowchart diagram of an exemplary torsion limited method according to the present specification; the Fig. 3 is a perspective view of an exemplary embodiment of a solar tracker according to the present specification; the Fig. 4 is an intricately carved view of an exemplary embodiment of a sun tracker including a torque limiter in accordance with the present specification; the Fig. 5 is a detailed cutaway view of an exemplary embodiment of a gear driven mechanical unit including a torque limiter in accordance with the present specification; the Fig. 6 is a perspective view of an exemplary embodiment of a friction plate torsion limiter in accordance with the present specification; the Fig. 7A is a perspective view of an exemplary embodiment of an individually powered solar tracker incorporating an exemplary torque limiter in accordance with the present specification; the Fig. 7B is a perspective view of the sun tracker of Fig. 7A; the Fig. 8 is a perspective view of an example embodiment of a chain gear driven sun tracker arrangement including an example torque limiting clutch in accordance with the present specification; the Fig. 9 is a perspective view of an exemplary embodiment of a balanced tracker system incorporating an exemplary embodiment of a rotational torque limiter in accordance with the present specification; the Fig. 10 is a perspective view of an exemplary embodiment of a balanced chained tracker system including an exemplary embodiment of a linear slide force limiter in accordance with the present specification; the Fig. 11 is a perspective view of an exemplary embodiment of a linear slide force limiter in accordance with the present specification; the Fig. 12A is a rear perspective view of an exemplary embodiment of a hydraulic ram-powered solar tracker including an exemplary overpressure valve in accordance with the present specification; the Fig. 12B is a side view of the sun tracker of Fig. 12A; the Fig. 13 is a perspective view of an exemplary embodiment of a hydraulic cylinder or ram in accordance with the present specification; the Fig. 14 is a cutaway view of an exemplary embodiment of an overpressure valve in accordance with the present specification; the Fig. 15 is a perspective view of an example embodiment of an example sun tracker and torque limiter gear assembly in accordance with the present specification; the Fig. 16 is a side view of an exemplary embodiment of an exemplary sun tracker and torque limiter gear assembly in accordance with the present specification; the Fig. 17 is a detailed view of an example embodiment of an example sun tracker and torque limiter gear assembly in accordance with the present specification; the Fig. 18 is a detailed side view of an example embodiment of an example sun tracker and torque limiter gear assembly in accordance with the present specification; the Fig. 19 is a perspective view of an example embodiment of a solar tracker including an example motor brake in accordance with the present specification; the Fig. 20 is a cutaway view of an exemplary embodiment of a motor brake in accordance with the present specification; the Fig. 21 is a notched perspective view of a DC brush motor used in accordance with the exemplary embodiments of the present specification; the Fig. 22 is a schematic diagram of an example motor frame reduction optimization method of a DC brush type motor for creating a motor brake in accordance with the present specification; the Fig. 23A is a perspective view of an exemplary embodiment of a limiting stop in accordance with the present specification; the Fig. 23B is a perspective view of an exemplary embodiment of the limit stop of FIG. 23A; the Fig. 23C is a perspective view of the limit stop of Fig. 23A; the Fig. 23D is a perspective view of the limit stop of Fig. 23A near an extreme position; the Fig. 24A is a perspective view of an exemplary embodiment of a limit stop in accordance with the present specification; the Fig. 24B is a side view of the limit stop of Fig. 24A; and Fig. 24C is a cross-sectional view of the limit stop of Fig. 24A.

DETAILED DESCRIPTION

[0029] In the following paragraphs, the modalities are described in detail as an example with reference to the accompanying drawings, which are not drawn to scale, and the illustrated components are not drawn proportionally to each other. Throughout the description, the modalities and examples presented should be considered as exemplary, rather than representing limitations of the present descriptive report. As used in this document, the expression “this descriptive report” refers to any of the modalities described in this document, and any of their equivalents. Furthermore, references to various aspects of the specification throughout this document do not imply that all claimed embodiments or methods must come to include all referenced aspects.

[0030] Exemplary embodiments of torsion limiters can be advantageously used in any type of drive system that may be exposed to external forces, such as high wind forces, and can benefit from the ability to withstand external force along with multiple points along the structure rather than just at a single point. Solar trackers comprise one example of such a system, and exemplary embodiments may be used on any type of solar tracker, including without limitation, single-axis trackers such as horizontal, tilt, and roll axis trackers, and for azimuth as well as dual axis trackers. Exemplary embodiments include any solar tracker model that includes a torque limiter connected between the transmission output and the collector array where the torque limiter delivers a preset level of torque force. Exemplary embodiments include solar trackers that are gear driven, hydraulically powered, or powered by any other mechanisms. Example tracker geometries incorporate a helical gear primary gear transmission, either attached directly to the tracker frame or through a secondary stage such as a spur gear track, D-ring chain drive, or cable system installed next to one or two column supports for the tracker. Example solar tracker embodiments may incorporate a balanced arrangement so that the torque limiter force remains constant across any tracker rotational angle.

[0031] The exemplary embodiments of the descriptive report release the torsion present in the tracking system so that the system moves out of a high torque position to a second position and stops, or if the external force is large enough, the system moves to an extreme position where there can be resistance against the torsional force at multiple points rather than at a single point, usually the center of the system. Alternatively, if the system encounters an obstruction, such as a sand dune, snow, ice, or some other external obstruction, torque from the system's drive motor is released from the input transmission by the torque limiter. Furthermore, in the connected driveway, only the row or rows that are affected by the obstruction do not move, while other unobstructed connected rows will continue within the track. Thus, exemplary embodiments advantageously provide with the benefit of releasing two different types of torque, external torsional forces from the wind and/or internal torsional forces generated by the transmission when the output of the tracking system is occluded.

[0032] In windy conditions, the force of the wind induces a pivot moment along the tracker system. If the pivot moment is greater than the torque limiter holding force, the torque limiter releases the torque and the tracker moves to the second position where the force can be dampened due to the gust of wind having been reduced or by the pivot moment has been reduced as a result of the new rotational position. If movement continues and the system is driven to the extreme position of multiple mechanical stops, then there may be wind resistance at multiple points rather than at a single point. Advantageously, systems employing exemplary embodiments of torsion limiters react in a neutral or passive manner, without the need to employ exemplary embodiments such as a motor or active release. In exemplary embodiments, the torque limiter consists of a clutch assembly that slips passively and introduces the opportunity for self-correction twice a day, once in the morning and once in the afternoon as the engine triggers the system to the extreme stop positions.

Conforme mencionado acima e descrito em maiores detalhes no documento, os limitadores de torção de exemplo e relacionados as transmissões de engrenagem e rastreadores solares reduzem ou eliminam o momento de articulação junto ao rastreador.[0033] Once the wind acts on an array tracked by PV, this wind normally causes the occurrence of a pivot moment MH around the rotational axis of the tracker as shown in Figures 1A-1D. The characteristics and factors of an example solar tracker subjected to wind action are designed as follows:

As mentioned above and described in greater detail in the document, example and related torsion limiters for gear transmissions and sun trackers reduce or eliminate pivotal moment with the tracker.

[0034] Fig. 2 shows an example method 1000 incorporating a torque limiter. A torsion limiter consists of any device that can limit, release, flatten, or otherwise reduce the level of torsion, torque, or any other external force on a system through any mechanism, including without limitation by, slip, uncoupling force, release pressure, ease of movement, or separating components of a system. As discussed in greater detail in this document, there are many variants of torque limiting designs. The system can be configured to have a pre-set threshold as to the level of torsion to which it can be safely exposed (1010). When an external force causes a torsion level next to the system exceeding the pre-set limit (1020), the torsion limiter acts to reduce the torsion level next to the system (1030). As discussed in greater detail in this document, depending on the type of torque limiter, the torque reducing action can be a slide (1040), a release pressure (1050), and/or facilitating rotational movement of the system in the direction of rotation. twist (1060).

[0035] In exemplary embodiments, when the system moves in the direction of torsion, it decouples the excess torsion so that the external force is released and the level of torsion next to the system is reduced (1070). In exemplary embodiments, moving the system in the twisting direction involves the system moving from a first position to at least a second position (1080). The system can reach a maximum position stop at at least a second position (1090). If the movement is a rotational movement, the maximum position stop may comprise a maximum angle of rotation (1100). Movement in the direction of twisting can occur from a first position to multiple positions (1110). In exemplary embodiments, the system is constrained at its maximum positions at multiple locations along a torsional resistance structure of the sun tracker assembly (1120).

[0036] With reference to Figures 3-5, there is a description of an example embodiment of a mechanical system driven by gear 10 and a torque limiter 18. The mechanical system driven by gear 10 can consist of any mechanical system type featuring one or more mechanical units and making use of gears to drive mechanical components aimed at rotating, moving and/or generating work, including, without any restriction, transport systems, agriculture systems, manufacturing systems and conversion systems energy and/or power generation. An exemplary gear-driven mechanical system 10 comprises at least one gear-driven mechanical unit 12 that includes a gear track 14. The mechanical system 10 may further include a gear drive system 16 that incorporates a torque limiter, such as as a torque limiting clutch 18. More particularly, an exemplary gear transmission system 16 comprises a torque limiting clutch 18 and a gear assembly 20 including at least one gear wheel 22.

[0037] A motor 15 can be provided for the transmission of the gear transmission system 16, which in turn rotates a beam or tube, for example, a torsion tube 34, directly, or drives a gear track 14, which in turn drives the torque tube or other module mounting beam structure 34. As illustrated in Fig. 3, the gear track 14 may consist of a spur gear track or D-ring chain drive, which comes to be fixed together with a rotational tube, for example a torsion tube 34, of the mechanical unit 12 In this way, when activated by the gear transmission system 16, a mechanical unit 12 rotates. first gear stage of the mechanical unit 12, and anterior to a location where the gear drive system 16 engages the gear track 14 of the mechanical unit 12. A second, third, etc., mechanical units, similar to the tracking assembly 12 can be connected to the transmission mechanical shaft 25 with a similar and separate helical assembly. This procedure can be repeated for several mechanical units in a gear driven mechanical system.

[0038] Turning attention to Figures 4 and 5, an example embodiment of a torque limiting clutch 18 can be seen in a notched sectional view of an example gearbox 24. The gear wheel 22 can comprise of any type of gear wheel and is shown, by way of example, as a helical wheel engaging with the helical thread 21. As can be seen in Fig. 5, the helical wheel 22 can define two conical sections 26 adjacent to the central part. In the exemplary embodiments, the clutch 18 is located next to these conical sections 26. In the exemplary embodiments, two steel filaments 26 may be present that engage the helical wheel gear 22 under spring tension. The clutch can be adjusted via a nut 44 or other equivalent mechanism that varies the spring tension along the filament 26. The mechanical gearbox output shaft 43 connects the gearbox 24 with the gear track 14. Exemplary embodiments, springs 19 are provided adjacent to the mechanical output shaft 43. The springs may be in the form of washers 19, such as Belleville washers. As can be seen in Fig. 5, the washers 19 consist of conical discs facing each other along the mechanical output shaft 13 on the outside of the gearbox 24. The washers 19 act as springs which provide the necessary pressure for the conical sections against the wheel helical 22.

[0039] When a torque level in gear system 29 exceeds a preset level, clutch 18 slips. More particularly, when the friction of the clutch 18 against the filaments 26 is overcome due to the increase in torque, the clutch 18 slips. This procedure advantageously releases the torque with the mechanical unit driven by gear 12. This torque release factor is particularly advantageous in exemplary embodiments where the mechanical units 12 are rotational due to the limitation of the HM articulation moment around the rotational axis of the units.

[0040] Various mechanical conditions may occur in exemplary embodiments of a clutch, gear transmission, and mechanical system containing one or more mechanical units, which may comprise of a solar tracking system that includes one or more trackers. With reference to Figures 1 and 3, an example solar tracker 12 comprises at least one support column 32, which can assume any format, being composed of any type of material as long as it is capable of supporting the PV modules or other components installed alongside them. Exemplary embodiments of a solar tracker 12 include two spaced apart support columns 32a and 32b. A torsion beam 34 or other tracker structure is connected to the support column 32. More particularly, the torsion beam connects the two support columns 32a, 32b and can be attached together with the support columns by means of a bearing. 36 and bearing housing layout including any suitable types of fasteners.

[0041] The torsion beam 34 can assume any shape or configuration suitable for supporting an assembly track or other type of assembly mechanism, including multiple connected beams, and in exemplary embodiments they have a cross section in a hexagonal, square or circular shape . In a system that features a suspended weight, the torque along with the suspended idle load varies as the system rotates. Alternative exemplary torsion beam embodiments can be configured having a balanced center of gravity, such as the weight of the arrangement being rotated about the balance point. This balanced system can be advantageous to incorporate with the torsion limitation model because, without the presence of any suspended weight, it will preserve the torsional release force along all rotational positions.

[0042] A pivot axis 40 extends through the torsion beam 34, and the torsion beam 34 can pivot or rotate around the pivot axis 40. The solar modules 42 can be installed next to the solar tracker 12, either installed on the torsion beam 34 using the grips 35 or via a module mounting bracket assembly. It should be noted that solar trackers may employ one or more torsion beams in a multi-beam torsion frame arrangement. In such embodiments, a tracker can have two or more torsion beams along its length. A row of multiple trackers may have two or more torsion beams acting along the length of the row.

[0043] In the exemplary embodiments, the gear transmission system 16 of the solar tracker 12 incorporates a torque limiting clutch 18 next to the first gear stage of the solar tracker 12. The exemplary embodiments may include a solar tracker driven by a stage gear unique where the gear transmission system 16 consists of a single stage helical gear transmission which directly rotates the array of solar collector rows. The torque limiter, in the form of a clutch, may be located between the worm gear transmission output connection and the solar collector array. Exemplary embodiments may also include two multistage solar trackers. Gear assembly 20 includes at least one gear wheel 22, in exemplary embodiments, the gear wheel comprises a helical wheel.

[0044] In exemplary embodiments, the torque limiting clutch 18 is located between the output connection of the helical gear first stage and the second stage gear. The second or multistage gear or gears may be constructed from any type of bidirectional gear transmission system capable of transmitting rotational force in a bidirectional direction, including without limitation a spur gear, pin gear, transmission cable or chain transmission. Torque limiting clutch 18 may be located adjacent to the output of the gear assembly 20, adjacent to the output of the first sun tracker gear stage 12, and anterior to a location where the gear drive system 16 engages with the track. of gear 14 of sun tracker 12. As discussed above, clutch 18 may be located on two tapered sections 26 of helical wheel gear 22. The two steel strands 26 engage helical wheel gear 22 under spring tension, which may be adjustable via nut 44 or other adjustment mechanism.

[0045] In exemplary embodiments, the torque limiting clutch can be incorporated together with a plurality of solar trackers 12 connected in an array profile comprising one or more rows 46 of solar trackers. More particularly, the multiple solar trackers 12 can be mechanically connected in a large configuration of arrays 50 so that they operate in unison, driven by a single motor and tracker controller. Row array configurations can be implemented by providing a threaded rotational transmission system below the solar tracker array. Another bearing system, such as a slewing drive, can also be incorporated into the fixed-tilt azimuth tracking geometry if properly designed to withstand the applied load forces near the base of the row arrangement support. In alternative exemplary embodiments, the arrangement may feature a motor for each solar collector gear drive. In single motorized gear transmission embodiments, a torque limiting factor can be incorporated along with the motorized gear transmission assembly. In exemplary embodiments, the transmission system may incorporate the helical gear transmission chained together with a carousel-type fixed inclined azimuthal tracking row arrangement field. In such embodiments, the inclined solar array is rotated within a large circular bearing over a wide area for tracking the sun.

[0046] Turning to Fig. 6, it is seen that an exemplary embodiment of a multi-plate, spring-force, high-torque torsion limiter 718 may be comprised of multiple interleaved spring-loaded friction plates 715. The springs 717 create a frictional force 715 causing an increase in the frictional surface area of the 718 torsion limiter. This model consists of an example variant of the spring-loaded filament conical torsion limiter described in Figures 4 and 5. The bore can be connected to a mechanical shaft and the outer diameter connected to a different mechanical axis. Torque limiter 718 restricts the torque present between the two mechanical shafts. The torque limiter can be incorporated within a helical gear drive unit between the gear core and the output as shown in Fig. 7B, or it can be installed on the outside of the helical gear unit at the torque tube connection next to the helical gear unit, as shown in Fig. 7A. Alternatively, it can be connected to the torque tube along the inside diameter and the linear arm to limit the torque together to arrange a chained tracking system, as given by Fig. 10.

[0047] Exemplary embodiments of the systems using clutch assemblies with torque limitation are shown as solar tracking systems as an example, in Figures 7A-12B. In these and other modalities, the torque limiting clutch can be present at a location other than the first gear stage of the tracker. Referring to Figures 7A, 7B and 8, an exemplary embodiment of an individually motorized gear driven solar tracker 112 may have a clutch 118 adjacent to the output of a gear assembly or incorporated within the drive unit 116. configured similarly to the example systems shown in Figures 3-4, where multiple trackers are driven by a single motor, and the torque limiting clutch 18 works in the same way, providing the same advantages. In an example solar tracker assembly 112, the torsion beam 34 is connected to the support column 32, and solar modules 42 can be installed on the tracker 112.

[0048] In an example embodiment, illustrated in Figures 7A and 7B, the torque limiter or clutch 118 can be located next to the output connection of the gear transmission unit 116 to the torque tube 34 of a driven solar tracker by gear 112 independently motorized. More particularly, the clutch 118 is mechanically connected to the output of the gear assembly (within the transmission unit 116). Alternatively, the clutch can be incorporated along with other stages of the gear train, such as between a brake motor and a two-way gear transmission. Additional torque limiting clutches 118 may be provided and, in exemplary embodiments, are located between a rotational actuator 111 and torsion beam 34 of tracker 112. In exemplary embodiments, transmission unit 116 houses a torque limiting clutch. Fig. 8 shows an exemplary embodiment of a single stage chained gear transmission tracker 112 arranged in multiple rows 46 where two torque limiting clutches 118 are positioned adjacent to the output of the main transmission gear 116.

[0049] Fig. 9 shows an exemplary embodiment of a balanced tracker 212 having a torque limiter 218 adjacent to the torque arm connection to the torque tube 34. In exemplary embodiments, a rotational clutch can be located in the main torque element or at the output of the gear of any type of tracker. As shown in Fig. 9, in exemplary embodiments, a torque limiter 218 may be incorporated between the gear drive unit output arm connection 216 and the torque tube 34 of a balanced tracker system. More particularly, the rotary clutch 218 is mechanically connected to the gear track 214 of the sun tracker 212, while the gear track 211 is operatively connected to the torsion beam 34. In exemplary embodiments, the torsion limiter may comprise a limiter rotary torsion.

[0050] With reference to Figures 10, 11, there is the presentation of an example embodiment of a balanced solar tracker 310. In the present case, the chain can incorporate a linear sliding force limiter 318 next to each tracker 312 to reach the single row movement to an extreme position during the presence of strong wind. An exemplary embodiment of a linear force limiter 318 shown in Fig. 11. In exemplary embodiments, the linear clutch consists of a linear friction slider 318 that enables the tracker to rotate while the linear chain slides in a linear motion. The linear friction slider 318 is comprised of a tube 319 and a gripper 321 as it slides over the tube. The grip 321 is installed adjacent to the tube via a trunnion bracket 323 and a friction fit 325 located between the grip 321 and the tube 319. The linear friction slider device 318 can be positioned in the balanced array of a solar tracker. When the torsional force externally applied to the tracker turns out to be greater than the force required to overcome the friction of slider 318, then the torsional force can be released and the tracker is able to move. It should be noted that a balanced tracker system can be individually driven or connected together with a linear transmission movement.

[0051] With reference to Figures 12A, 12B, 13 and 14, exemplary embodiments of hydraulically powered tracker systems 412 may employ a torsional relief function in the form of an excessive pressure release valve 418 providing conditions for the tracker 412 to move to an extreme position within conditions where the tracker is exposed to excess wind force. A double-acting hydraulic ram 460, or cylinder, as shown in Fig. 13, may be employed to actuate the hydraulic tracker 412. Exemplary embodiments of a hydraulic ram 460 feature a rod 461, which may comprise a seal, rod 465 and other sealing components 463, an extension port 462, and a retractable port 464 The linear motion of hydraulic ram 160 can be converted to rotary motion and utilized in a balanced tracker model, discussed above with reference to Figures 10-11.

[0052] In exemplary embodiments, the hydraulic ram 460 can be fitted with an overpressure valve 418, such as that shown in Fig. 14. An exemplary overpressure valve 418 has a spring 472 contained within valve bonnet 476. A seat disc 478 is retained by a disc retainer 480 within body 474. Valve 418 may further comprise of a discharge adjustment ring 482 and a nozzle 484. The overpressure valve 418 can be incorporated in the hydraulic fluid circuit between the two chambers of the hydraulic ram 460 effecting the positioning and retention of the rotational position, that is, it can be located between the extension port 462 and the retractable port 464 of the hydraulic ram 460.

[0053] This makes it possible to move along with the 460 ram when the external application of torque on the tracker system creates excessive pressure on the hydraulic ram. More particularly, when enough pressure comes to the overpressure valve 418, it effects hydraulic release, acting as a torque limiter for the crawler. Excess Pressure Relief Valve 418 is designed or set to open at a preset pressure with externally applied excess torque release along with tracking system 412. Pressure is released by providing conditions that the pressurized fluid flows between the two chambers of the hydraulic ram, with the pressure being controlled by valve 418. A pneumatically driven tracker system may further employ a wind-induced torsion relief in the form of an excess pressure release valve to reach the same function.

[0054] Exemplary embodiments of a motorized tracker/gear track assembly are described below with reference to Figures 15-18. A gear track 814 is coupled to the torsion tube 831 of a solar tracker assembly 812 and may also be attached to a support column 832 of the tracker assembly. More particularly, gear track 814 may be attached adjacent to torque tube 834 via torque tube bearing assemblies 836 and coupler 823. In exemplary embodiments, gear case 824 has an internal clutch (not shown) located adjacent to it. to an output of the gear assembly 820, which includes the gear rail 814, a pinion gear 815 containing the pinion gear mechanical shaft 817, and may include a gear mechanical shaft end bearing. The system may have an upright gear transmission column assembly containing a transmission motor 821 for driving the gearbox 824. One or more photovoltaic modules 842 may be attached to the torsion tube 834 using installation brackets 835.

[0055] Fig. 17 shows a detailed view of the travel position at the end of the gear track 814 and the engagement of the pinion gear 815. In exemplary embodiments, the pins 825 of the gear track 814 are advantageously positioned at or near the end of the gear track. gear 814 to effect a stop as pinion gear 815 moves to the altered placement of pins 825. As best seen in FIG. 18, the pinion gear 815 may have central ridge pins 825 and a castellated pinion gear. This arrangement has the advantage of ensuring that the pinion gear 815 contacts only the pins 825 of the gear track 814 and not the side plates of the gear track.

[0056] Turning attention to Figures 19, 22, in exemplary embodiments, a simple motorized solar tracker 512 incorporates a torque limiter device that can comprise a motor brake 518. As can be best seen in Fig. 20, an example motor brake would be attached to an electric motor. The 518 motor brake can include any suitable combination of pressure plate and disc components. In exemplary embodiments, the internal components include a stationary disk 521 as well as one or more rotational friction disks 523 having a wheel hub and mechanical axle. The brake is electrically released during engine operation and engaged when the engine is de-energized. A pressure plate 525 acts forcing against the disks and a self-adjusting mechanism 527 can be provided to adjust the pressure against the disks. A 529 release lever allows for manual pressure release.

[0057] In the exemplary embodiments, an individual engine can be located next to each row. In exemplary embodiments, a gear system that is capable of being driven bidirectionally may be coupled together with a motor and motor brake 518 in each row. The motor may have a brake in the motor system or be used as a brake itself. Through proper motor, brake and gear sizing and gear deficiency, the motor or 518 motor brake can act as the attenuation of the wind force in the system. In exemplary embodiments, the transmission system comprises a bidirectional gear box 514, and the motor brake 518 is located next to the input of the gearbox 514. The bidirectional gear can be driven from the input or output of the gearbox. gear featuring the ability to be driven from both the output and input. In exemplary embodiments, the bidirectional gear may consist of any suitable gear, including without limitation a spur gear, helical gear, planetary gear, high-efficiency helical idle gear, belt drive, chain drive, or other types. of bidirectional transmission arrangements.

[0058] In the example engine brake arrangements, the torque on the torsion tube 34, applied according to the action by external forces, such as the wind, is reduced by the gearshift or the bidirectional gear, which overcome the engine brake force. Then the twist is released at the outlet by rotating the tracker row. In this embodiment, the motor brake 518 is configured to lock the solar tracker 512 in position until a preset torque limit is reached, at which time the motor brake slips. Exemplary embodiments may incorporate a mechanical brake within the motor or be affixed between the motor and the gear transmission. If the motor itself has a separate brake, as shown in Fig. 21, then the motor can be sized for moving the row arrangement separately from the torque release force required to retain the row arrangement.

[0059] As shown in Fig. 21, the motor brake may be a direct current brush motor type 618 that has power input leads, such as lead wires 635, causing shorts to promote braking action at the motor output. If designed to contain a brush-type motor with direct current and properly sized with shift gears and slip torque, the motor itself can be used as a slip clutch to overcome the presence of external torsion. A DC 618 brush type motor containing its power leads in short sets acts as a brake by driving the motor in the form of a generator presenting a shorted output, making it difficult for the motor to work. In exemplary embodiments, the brush-type motor 618 has an internal switch 631 for periodically reversing the current direction and at least one brush 633 in contact with the switch to terminate the switch.

[0060] There is the illustration in Fig. 22 of an example circuit diagram showing the embodiment of a motor. Fig. 22 presents an example method of shorting the output of a motor, where in this example mode, the brush motor 618 acts as a shorted output generator. The H-Gate component drives the motor, and the short on the motor output can be performed via relay 619. When this happens, the brush motor 618 acts as a generator with full load, making the transmission difficult, starting to act as a brake next to the solar tracker system. Motor 618 may incorporate a brake 637, which may consist of a negative actuation type electromagnetic brake. It should be noted that a motor brake can be incorporated into any of a variety of solar tracker assemblies, including without restriction a simple individually motorized system, a bi-directional gear driven system or a multi-stage system. When an external force causes a level of torsion along the transmission system to exceed the pre-established limit, the engine brake is overcome and facilitates the spare drive of the transmission system.

[0061] Turning attention to Figures 23A-23D, there is a description of an example embodiment of a bearing stop assembly 70. An example bearing stop assembly 70 consists of a bearing housing 72, a sliding bearing section 74 and an internal rotatable stop block 76. Fig. 23B depicts stop block 76 engaged along one side of its rotation limit, i.e., an extreme stop position. Fig. 23C shows the stop block 76 in the intermediate position, that is, in the intermediate part of the rotational movement made possible. Fig. 23D shows the stop block 76 near the stop position at the opposite end of Fig. 23B. The bearing stop assemblies can be positioned adjacent to each column and can be attached to the torque tube 34. The bearing stop assemblies 70 advantageously provide the triple function of supporting the solar tracker row, providing with a bearing where the row can rotate, and, as discussed in detail in this document, and function as mechanical stops along the maximum rotational positions of the trackers. The housing can be lined with a low-friction coating to prevent slipping or snagging around slow-moving bearings.

[0062] Figures 24A-24C illustrate other exemplary embodiments of a tracker bearing stop assembly 170 with integral grounding. An exemplary assembly 170 comprises a bearing housing 172, a pin and roller bearing wheels 173, a dry sliding top half bushing liner 174, and an internally rotating stop block 176. Advantageously, this model can provide better performance in dusty environments and also provide a continuously electrically conductive ground path, eliminating the need for an external ground wire to electrically bond the torque tube to the column.

[0063] With reference again to Fig. 23A, an example embodiment of a bearing stop assembly 70 can be seen fully installed in the solar tracker application where the solar tracker 12 has photovoltaic modules 42 installed next to the torsion tube 34 containing installation brackets in a special module. An additional bracket can be provided to enable the connection of a damper to be connected between the torsion tube 34 and the support column 32 of the tracker. A damper can be incorporated alongside the gear drive to control the crawler's rotation rate during eventual excessive torque. When the torsion is relieved by allowing the system to rotate, the speed at which the row is allowed to move can be controlled by the sliding friction of the clutch, or through an external damper, or both.

[0064] In exemplary embodiments, the bearing stop assembly 70 is connected together with a U-brace 78 connecting to an I-beam column 80. As shown, the bearing stop set 70 is installed together to an example octagonal torque tube 34, so that the torque tube runs through the center portion of the bearing stop assembly. It should be noted that the torque tube may consist of any shape in cross section including without limitation circular, round, oval, square, rectangular, triangular or pentagonal, hexagonal, and octagonal. The stop block 76 in the bearing stop assembly 70 can be shaped into a ring to conform to the shape of the outside of the torque tube 34 so as to be ground on the outside of the tube and rotate with the tube.

[0065] In the exemplary embodiments, the dry sliding bearing 74 also adjusts to the shape of the external part of the torsion tube 34 and rotates with the tube. As shown in Fig. 23A, the dry slide bearing 74 may be octagonal on the inside and round on the outside. The round outer shape of the dry sliding bearing 74 slides over the round inner shape of the bearing housing 72. This interface of the outer surface of the dry sliding bearing 74 and the inner surface of the bearing housing 72 forms the bearing surface. In exemplary embodiments, the bearing surface of bearing housing 72 may be coated with a low friction coating to reduce bearing friction. The dry slide bearing 74 is typically formed from polymeric material and may also incorporate friction reducing agents into its composition to reduce friction. When the torque tube 34 is rotated to its mechanical limits, the stop block 76 engages with the bearing housing to eliminate further rotation of the torque tube 34. There are therefore two extreme rotational stop positions created by the block stop 76.

[0100] In operation, the wind induces a moment of articulation MH next to the mechanical system driven by gear. With reference to Figures 1 through 5 and other illustrative embodiments, the clutch can be preset to slip for a fraction of the maximum induced pivot moment torque. When the wind-induced pivot moment HM reaches the pre-set torque limit value, the friction of the clutch 18 together with the filaments 26 is overcome, and the clutch 18 slips. pressure for the wind-induced pivot moment MH, advantageously releasing torque together with the mechanical unit driven by gear 12. With sufficient torque level to slip the clutch, a row of mechanical units driven by gear 12 can swing out position and into a lower pivot moment position.

[0101] When the torsion exerted externally at the output of the gear transmission system (the arrangement of rows of collectors) exceeds a pre-set limit, the torque limitation device provides conditions for the arrangement of rows to move to a new position until the force has dropped below the torsion limit or the row arrangement has reached its mechanical limits. In the case where the twist exerted from the inlet exceeds the pre-set torsion limit together with the arrangement, the twist limiting device decouples the excess inlet force and enables the inlet to move without affecting the movement of the row arrangement. . As discussed in greater detail in this document, this can be used to synchronize chained rows when driven against a mechanical stop, or used when natural occurrences such as snow or sand shifts prevent movement of the row arrangement. In this case, it is advantageous to decouple the transmission forces entering with the torsion limiter and retaining the positioning of the row arrangement outputs.

[0102] In exemplary embodiments, when wind speed forces exceed the torque required to slip the clutch in the drive train, then the solar array or the mechanical gear drive unit 12 rotates to another position. If this excess torque is carried on by the wind, then each mechanical unit 12 and array 50 of units moves to its maximum angle of rotation 54, an extreme rotational angle where there can be resistance to torsional force in front of multiple locations adjacent to the torque tube 34. The row of mechanical units 17 can be rotated by the wind until the maximum stopping angle is reached.

[0103] In exemplary embodiments, the system can reach the mechanical stops 59 in each row of mechanical units 12, each time the row is moved to an extreme position during normal operation. Allowing external forces to rotate the row of solar trackers while activating the other rows of solar trackers giving conditions for each row to reach its maximum limit position until all rows of solar trackers are aligned. Advantageously, this ensures alignment of all rows of units 12 twice a day in the event that the wind moves a row. This ensures that all rows are exactly synchronized at least once a day. When carrying out a new project, the rows of the tracker can be pointed in all directions, but after calibration, the rows must be completely synchronized. It should be noted that in a chained solar tracker system, the clutch 18 can act independently along each tracker row. This is due to the fact that having a chained system with a spare drive having to carry out the spare transmission along all the rows of trackers, it may not react properly to protect each row when the wind force comes to act individually along the each row.

[0104] In the exemplary embodiments, the rotational speed can be regulated by the clutch slip force. Advantageously, clutch 18 can decouple dynamic loads within the system by eliminating the spring in the system, significantly reducing design loads. Alternatively, dampers 58 can be provided to slow down the tracker's movement. Maximum angle stop resistance can be made not only by the gear track, but by the dampers adjacent to the gear track or stops 58 at the end of the rows of the mechanical units 12, thus sharing the torsional load of the gear track 60 and distributing the torsional load across multiple points along the torsion tube 34. The dampers 58 can serve as dual-duty components, as end-of-row stops, or as dampers along any location they may be designed to serve. the regulation of torsional release reaction velocity and resisting pivotal moment loads.

[0105] Advantageously, the exemplary embodiments reduce the maximum pivot moment, eliminating the dynamic load, and giving conditions for gear-driven mechanical systems to resist the pivot moment forces along the multiple points on the row instead of along one single point. Typically, the forces of articulation moment are greater with smaller inclination angles and reduced with row arrangement where the inclination angles increase. In the exemplary modalities, in front of the extreme vertical stop positions, the maximum pivot moment force will be smaller than in front of small rotation angles and will only occur in front of mechanical stops close to the range of movement extremes. There may be more resistance to the total pivot moment than just the center gear. The range of mechanical movement stops can be placed at any location along the row arrangement, typically in front of distributed vertical supports, to meet pivotal moment loading resistance, thus minimizing torsional loads along any single point in the system.

[0106] With reference again to Figures 1 and 3, the maximum pivot moment can comprise x feet pounds, and clutch 18 slips around x/4 feet pounds. Consequently, the torque tube 34 need only withstand a maximum load of x/4 ft. pounds at the gear drive 16 before clutch 18 slips. In this exemplary embodiment, at the maximum angle of rotation 54, the maximum pivot moment is about x feet pounds, the gear resists x/2 feet pounds, and the stops located near the ends of the tracker must withstand x/4 feet pounds so that the maximum torsional load on tube 34 is x/4 foot pounds. Maximum torque values should probably be doubled on each component without advantageously employing exemplary clutch and multistop embodiments. These values can be further reduced by allowing for the release of torsion to occur at lower values and by using more stops than just near the ends of the row arrangement, such as for each column.

[0107] In exemplary embodiments, the transmission line and the gear track could not see a gear track 14 stopping the force coming from the motor 15. Consequently, the gear track and the transmission line can have a more minimized construction. Furthermore, example systems not only need to be built to observe movement restricted to each day's range of motion, but may also be incorporated to protect against excessive travel along with the torque limiter. The dampers 38 and the gear track 14 can be optimally designed and implemented for the entire range of implementation. No extra allowance is required for the movement range beyond that for the daily movement range.

[0108] Advantageously, in the exemplary embodiments, if a row of mechanical units 12 has a mechanical connection, it will not influence the rest of the system 10. This can be useful for carrying out self-diagnostics regarding the existence of connection problems with the tracker row. If the outer rows move to an extreme angle from the wind, then they can act as a wind block along with the inner rows. Due to the lifting forces, drag and articulation moment occurring in combination with the system and each of these loads can present peaks in different positions of specific rotational angles, it can become advantageous to provide conditions for a row of mechanical units to move together to a more extreme angle position before the maximum lift force condition occurs. If this is reliably accomplished via the torsion limiters discussed in this report, then the foundation model value for maximum uplift will be less and therefore the size and/or depth required for the system foundation can be reduced to provide strength resistance. lower uplift.

[0109] The torsional strength requirements may be lower since resistance can be offered in front of multiple points and not in front of the maximum rotational angle for the peak pivot moment. The peak drag force may not change as the system typically comes to be designed for the extreme rotational angular position in the case of horizontal solar trackers and may be downgraded in other solar tracker geometries. These strength reductions equate to reductions in the structural requirements of mechanical systems. A reduction in structural material typically equates to substantial material cost savings and may also equate to labor savings, thereby reducing the total cost of the installed system.

[0110] Thus, it should be noted that devices, systems and torsion limiting methods incorporated into the systems, such as solar trackers, are provided. Although the systems, devices and methods have been described in terms of exemplary embodiments, it should be understood that the specification need not be limited to the described embodiments. Although illustrated embodiments have been described above, it should be apparent to those skilled in the art that various changes and modifications can be effected without deviating from this specification.

[0111] It should be noted that any of the foregoing configurations and specialized components or chemical compounds may be employed interchangeably with any of the foregoing embodiment systems. It is intended to cover various modifications and similar provisions included within the spirit and scope of the claims, the scope of which must be in accordance with the broader interpretation in order to include all types of modifications and similar structures. The present specification includes any and all embodiments of the claims hereafter that fall within the true spirit and scope of the specification.

Claims (17)

1. Solar tracker assembly, characterized in that it comprises: a support column (32); one or more torque tubes or torsion beams (34) connected to the support column; an installation mechanism attached to one or more torque tubes or torsion beams; a drive system connected to one or more torque tubes or torque beams; and a torque limiter connected to an output of the drive system; wherein when a pivot moment force causes a torque level in the drive system to exceed a preset limit, the torque limiter passively facilitates rotational movement of the sun tracker assembly in the direction of the torque, thereby allowing the moment force to pivots rotate the solar tracker assembly about a pivot axis to a lower position than the pivot moment. 2. Solar tracker assembly, according to claim 1, characterized in that the movement in the direction of the torque decouples the excess torque so that the external force is released and the level of torsion in the solar tracker assembly is reduced . 3. Solar tracker assembly according to claim 2, characterized in that the movement in the direction of the torque comprises moving the solar tracker assembly from a first rotational position to at least a second rotational position. 4. Solar tracker assembly, according to claim 3, characterized in that it additionally comprises one or more mechanical stops connected to the support column (32), the mechanical stops being located in the maximum rotational position of the solar tracker; wherein the solar tracker assembly reaches a maximum stop position at the at least a second rotational position. 5. Solar tracker assembly according to claim 3, characterized in that the solar tracker assembly is constrained in their maximum rotational positions at multiple locations distributed along a torsional structure of resistance of the solar tracker assembly. 6. Solar tracker assembly according to claim 1, characterized in that the solar tracker assembly comprises a plurality of support columns for supporting a row of trackers and further comprises a stop on each support column. 7. Solar tracker assembly, according to claim 6, characterized in that the stops limit the torque on the support column when each tracker in the row reaches its maximum rotational position. 8. Solar tracker assembly, according to claim 1, characterized in that the drive system comprises a gear assembly comprising at least one gear wheel. 9. Solar tracker set according to claim 8, characterized in that the gear set comprises a unidirectional gear box and the torque limiter is a torque limiting clutch contained within the gear box. 10. Solar tracker assembly according to claim 8, characterized in that the gear assembly comprises a friction coupling engaging the gear wheel and the torque limiter is located in the friction coupling. 11. Solar tracker set according to claim 8, characterized in that the torque limiter is located at the output of the first gear stage of the gear set. 12. Solar tracker assembly according to claim 1, characterized in that the solar tracker assembly consists of a push/pull chained tracker and the torque limiter is a linear sliding device. 13. Solar tracker set according to claim 1, characterized in that the solar tracker set includes a hydraulic system and the torque limiter is a pressure release valve. 14. Solar tracker set according to claim 1, characterized in that it additionally comprises a damper to control the release of torsional force and slow down the movement of the solar tracker set. 15. Solar tracker assembly according to claim 1, characterized in that the one or more torque tubes or torsion beam are configured with a balanced center of gravity so that one or more of the torque tubes or beams of torsion rotate around the balanced center of gravity. 16. The solar tracker assembly of claim 1, characterized in that the solar tracker assembly comprises a plurality of support columns supporting a plurality of rows of solar trackers; wherein when there is an obstruction obstructing one or more rows of sun trackers, the torque limiter stops rotational movement of the obstructed row while allowing the unobstructed rows to continue to rotate to track the sun. 17. Solar tracker assembly, characterized in that it comprises: a support column; or more torque tubes or torsion beams connected to the support column; mounting mechanism attached to one or more torque tubes or torsion beams; a drive system connected to the one or more torque tubes or torsion beams, the drive system comprising a bidirectional gearbox having an inlet and an outlet; and engine brake located at the input of the bidirectional gearbox; wherein when a pivot moment force causes a torque level to the drive system to exceed a predetermined limit, the engine brake slips to facilitate reverse drive of the drive system, thus allowing the pivot moment force to rotate the tracker assembly solar panels to a lower pivot moment position.

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